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1144 P. Garg et al. / Energy Procedia 49 (2014) 1138 – 1146 more or less comparable for both the cycles, VFRturbine,outlet for steam cycle is about 100 times higher than corresponding CO2 cycle. In general, turbine exhaust corresponds to the largest specific volume and hence, the maximum VFR at this location in any power cycle. Decrease in it may result in scaling down the whole plant. In the present case, we use this observation to estimate the turbine exhaust pipeline cross sectional area at p2’ =300 bar and T3’ =873 K for both the cycles. For the identical turbine exhaust velocities, the ratio of their VFRturbine,outlet provides the information about pipeline area ratios required for both the working fluids. It is found that cross sectional area of steam pipeline should be ~179 larger than a CO2 pipeline. As a result, the diameter of a CO2 pipeline turns out to be ~1/7th of a steam pipeline. This simple exercise reveals the fact that TC-CO2 power plant will be notably compact than corresponding TC-steam plant. Further, a detailed heat transfer analysis is needed to throw some light on the individual component sizes in the two cycles. For example, in case when air is used as a cooling media in the condenser of any power cycle; generally, heat transfer coefficient on air-side is found to dictate its size. In our case, although, condenser loads and overall heat transfer coefficients are comparable for both the cycles, higher LMTD across the condenser of TC-CO2 cycle will result in smaller heat transfer area. In addition, higher packing density of condensing tubes can be achieved in TC-CO2 cycle to further reduce the condenser size. 10 10,000 8 6 4 2 1,000 100 10 01 500 600 700 800 900 1000 Source temperature (K) Fig. 6. Turbine inlet and outlet volumetric flow rate for various source temperature at T1 = 300 K and p2’ = 300 bar. Legend: VFRturbine,inlet (left ordinate), VFRturbine,outlet (right ordinate), ◊ TC-steam cycle, x TC-CO2 cycle 3.2. Irreversibility analysis To account for losses in the various components of a power plant, detailed irreversibility analysis is needed. Irreversibility trend for both the cycles are presented in Figs. 7 and 8 for various source temperatures. High side pressure and sink temperature are fixed at 300 bar and T1 =300 K. Referring to Fig. 7, we observe that all components except regenerator show a diminishing trend in irreversibility with increase in T3. This is because of the fact that mass flow rate required to generate the given capacity decreases, so does the irreversibility. However, in the case of a regenerator, amount of heat transferred across finite temperature difference increases resulting in higher irreversibility. For steam cycle, irreversibility in turbine, pump and condenser show minimal variation with source temperature. Increasing irreversibility in heater is analogues to the regenerator in the CO2 cycle. A distinct feature of both the cycles is trend of total irreversibility generation with source temperature. While it decreases for CO2 cycle indicating improvement in cycle performance, same is not true for steam cycle. However, total irreversibility generation for both cycles is more or less identical at T3 = 1000 K. Fig. 8 provides information about component wise distribution of irreversibility for both the cycles at p2’ =300 bar, T1 =300 K and T3 =1000 K. The components are characterized based on the thermodynamic process. Pump and turbine are classified as power block elements in which isentropic processes are desirable. Rest of the components like condenser, heater and regenerator (only in case of CO2 cycle) are groups as heat exchangers. For a TC-steam cycle, losses in power block are found to be 59 % compared to 36 % in case of a TC-CO2 cycle. Irreversibility in power block elements depends on the isentropic efficiencies of turbo-machinery. Whereas in the case of heat exchangers, total heat addition in heater and regenerator results in 55 % availability losses in a TC- CO2 cycle VFRturbine,inlet (lps) VFRturbine,outlet (lps)PDF Image | CO2 steam in transcritical Rankine cycles concentrated solar
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